CN101581341A - Adjustment mechanism for inserting and extracting a separation coupling with rotating curve segment - Google Patents
Adjustment mechanism for inserting and extracting a separation coupling with rotating curve segment Download PDFInfo
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- CN101581341A CN101581341A CNA2009102039310A CN200910203931A CN101581341A CN 101581341 A CN101581341 A CN 101581341A CN A2009102039310 A CNA2009102039310 A CN A2009102039310A CN 200910203931 A CN200910203931 A CN 200910203931A CN 101581341 A CN101581341 A CN 101581341A
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- actuating mechanism
- cam part
- clutch
- rotation
- actuator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D28/00—Electrically-actuated clutches
Abstract
The present invention relates to an actuator mechanism for inserting and extracting a separation clutch (11) of single-clutch transmission or complex clutch transmission (10), the clutch has a housing for motor vehicle, the actuator mechanism comprises: an actuator driver (32), a cam component (36) comprising a curved recess (40), which is rotatable around a housing fixed bearing (38), and may rotate along a inserting rotation direction (50) or a extracting direction (54) through the actuator driver (32); and an inserting fork (42) capable of rotating around the second support member (44), which is fixed relative to the housing, and an end of the fork (42) is connected to a cam component (36) through an end of the cam follower (46), relative end of the fork is connected is connected to a the cam component (36) and the end of the fork is connected to the clutch (11) such that the clutch (11) closes when the curve segment rotates in rotation direction (50) and the cam component (36) opens when rotating along the extracting rotation (54). In rotation of the cam component (36), the cam follower (46) joints into the curved recess (40) and is guided by profile of the same; the profile is molded such that the cam follower (46) radially offsets along the cam component (36).
Description
Technical field
The present invention relates to a kind of actuating mechanism that is used to engage and throw off the disconnect-type clutch of single clutch speed changer or multiple clutch speed-changer, this speed changer has the housing that is used for motor vehicle.
Background technique
Various schemes by actuator devices joint and disengagement disconnect-type clutch are known.
First kind of scheme based on revolving valve described among the WO2007/096212A1.A problem of described solution is that by eccentric external force and big big hysteresis effect and friction that component caused thereof described component laterally acts on respect to the joint supporting direction of action.
Another problem is, for example, traditional actuator will stretch out quite long distance from case of transmission, this with regard to make such actuator be difficult to be used to connect use and have before in the speed changer of horizontal layout.
In paper " Elektromotorische Aktuatorik f ü rDoppelkupplungsgetriebe-Bester Wirkungsgrad aus eigenemAntrieb " [" Electromotive actuating arrangement for dual-clutchtransmission-best efficiency from a separate drive "] (LuK forum, 2006,136-143 page or leaf) in another kind of scheme has been described.Described paper proposes a kind of actuator, and the structure of this actuator is radially stretched from transmission input shaft and left, and this actuator is pressed in by circulating ball on the engine lever of clutch so that near described clutch.Here, engine lever extends on the inclined-plane.In order to allow clutch to open automatically, the clutch quilt is along disengaged direction preload.When clutch will be held when cutting out, must be always to power electric motors.And the actuator of actuating unit will stretch out the quite long distance of case of transmission, and this is most important for available installing space, and is particularly all the more so in series connection is used.
Another kind of double clutch actuator devices has been described in document DE102007003338A1.Have big installing space in the same requirement of the actuator devices shown in the described document, make that the integrated of described actuator devices is very difficult equally from space angle.
Summary of the invention
Therefore the purpose of this invention is to provide a kind of actuating mechanism, it can generally be used for single clutch and double clutch, and wherein required installing space is very little.Want to provide low friction valve in particular.This actuating mechanism should preferably have low power or energy requirement.Also wish to use the least possible parts, so that actuator devices can be simpler design usually.
Described purpose realizes by a kind of actuating mechanism that is used to engage and throws off the disconnect-type clutch of single clutch speed changer or dual-clutch transmission, this speed changer has housing and is adapted at using in the motor vehicle, and wherein actuating mechanism comprises: actuator; Cam part; Engage shift fork; And the cam follower that connects the joint shift fork.Cam part has arc groove.Described cam part can be around the rotation of first supporting member, and described first supporting member is fixed with respect to housing, and described cam part can be by actuator along engaging sense of rotation or throwing off the sense of rotation rotation.Engaging shift fork can be around the rotation of second supporting member, and described second supporting member is fixed with respect to housing.One side of described joint shift fork is connected to cam part by cam follower.The opposite side of shift fork is connected to disconnect-type clutch, so that disconnect-type clutch is closed and open when throwing off the sense of rotation rotation at cam part when engaging the sense of rotation rotation at cam part.Cam follower engages in the arc groove.When cam part rotated, cam follower was by the profile guiding of arc groove.When actuator activated, profile was formed as and makes the radial deflection of cam follower along cam part.
Actuating mechanism of the present invention has the advantage of simplicity of design.Be used to engage or parts that holdback clutch is required seldom.This actuating mechanism both can be installed in and also can be installed in the single clutch in the double clutch, but was that two covers are installed under the situation of double clutch.This actuating mechanism can use with wet clutch or dry clutch.
The structure of actuating mechanism of the present invention is very little.Even actuator can tangentially be integrated in the case of transmission and therefore also only can stretch out very short distance with respect to the inside housing that stretches out in the footpath of disconnect-type clutch axle.Especially favourable in the speed changer of this horizontal layout before series connection is used and had, particularly radially available installing space is very limited in these speed changers.The speed changer that is exclusively used in the series connection application often is integrated in the speed changer passage of small-sized (sparsely-dimensioned), and this is unchallenged for actuating mechanism according to the present invention.
If the extending circumferentially of the basic upper edge of the groove of cam part cam part also has the radius of variation, also is favourable.
By described measure, can guarantee at cam part that when its supporting member rotates engaging shift fork can be around its supporting member rotation to engage or holdback clutch.
Especially, groove has the contact side, this contact side in actuating mechanism is installed to speed changer the time owing to act on the preload on the disconnect-type clutch and contact with cam follower along the disconnect-type clutch disengaged direction.
Described measure has the effect of the contact side of all the time cam follower being pressed to cam part basically.Favourable selection by the contact side view, might constantly for example when arriving engagement positio, influence in some of movement process and be used for the required actuation motion of rotating cam parts in the mode of any desired, for example described actuation motion when being about to arrive the bonding point by (extraly) increase.
According to a kind of preferred implementation, the contact side has the particularly cross section of archimedes type spiral shape of one section spiral shape basically.
The derivation helical is a constant with respect to the math equation gained result of angle of rotation Phi in cylindrical coordinate system.This means that the power that acts on the disconnect-type clutch applies in constant mode.Therefore, the angle of rotation of cam part and be linear relationship between the translational motion with respect to cam part radially, cam follower is followed this relation approx.Self evidently be, also can use other spiral shape such as logarithmic spiral for example for the shape for the contact side supplies a model.
In the present invention further improved, the contacting side mask had continuous working portion, and working portion has the bonding point and has drop-outs in the zone at its other end in the zone of one end.
If the contact side has the convex surface that preferred radius is constant (in the reference system of cam part) in the zone, bonding point, also be favourable.
If cam part is rotated excessively along engaging sense of rotation, that is to say that cam follower crossed the bonding point, so just can reduce being applied on the disconnect-type clutch disconnect-type clutch is remained on the power of jointing state.Reduced thus and applied the required energy of described confining force.The load that actuating mechanism bears usually reduces, and this makes wear extent reduce.Especially, the load of actuator motor and the situation of comparing high load before are still less.The energy that consumes also still less.
According to further improvement, in abutting connection with working portion, described lateral parts has the protuberance that merges basically to go in the lock section to the lateral parts with protuberance along disengaged direction.
Utilize the contact side of respective design, particularly under the situation of dual-clutch transmission, might realize the lock function that stops.By " cross pushed away ", so described cam follower must be crossed protuberance in the side to lock subsequently in the additional convex surface to cam follower in the zone at bonding point.Under described situation, two gears are engaged in dual-clutch transmission, and this state of rest at speed changer is just possible.If speed changer is applied torque subsequently, so whole speed changer all can be propped up.Thus, speed changer and power train just can not be moved again.Described operator scheme can be used under static state that is to say and particularly stop vehicle safely in the time will stopping described vehicle.
According to further embodiment, actuating mechanism also has force compensating equipment, and its one or more parts to mechanism apply assistance force or auxiliary movement.Especially, might apply auxiliary movement to cam part, this action increases along with the increase of stroke in the direction of engagement ideally, is used to activate clutch and ever-increasing active force with compensation.
Utilize described measure, reduced to apply the power that is used for engaging clutch.Traditionally, described power is only applied separately by the motor of actuator.By corresponding force compensating, the power that is applied by motor is reduced.When holdback clutch, because clutch preferably in disengaged direction preload, therefore correspondingly need to apply the power reverse with force compensating equipment, but this power is particularly applied by its leaf spring by clutch self substantially.
In further preferred the improvement, force compensating equipment has spring element, and it is by along the reverse preload of throwing off sense of rotation, and an end of this spring element is connected to housing, and the opposite end is connected to cam part or shift fork.
Spring is as the power memory unit, so that auxiliary force to be provided during engaging process.During throwing off, auxiliary force is stored in the spring once more.
If the time along the rotation of joint sense of rotation, the protuberance of rising is set in the outer surface for the power that applies maximum possible on the cam part in the zone, bonding point at cam part, also be favourable.
Thus, auxiliary force can increase once more, particularly in the zone at bonding point, must apply maximum power at this for engaging clutch, and described auxiliary force helps the motor of actuator thus, thereby alleviates its load.
If cam follower is preferably rotatably to be fixed on shift fork roller between two prongs of shift fork and its diameter to be selected as making the shift fork roller to move by the play with predetermined extent along the contact side of arc groove, that also is favourable.
If actuator has motor (particularly having electric motor) and break, also is favourable.
In case clutch, motor are responsible for the confining force that provides required usually.If break is set now, the confining force that is provided by motor just might significantly reduce so.Test has shown that in order to utilize motor to apply confining force needing the maximum number magnitude is the electric current of 40A.On the contrary, for the identical confining force that applies, the electric current that the break of insertion needs has been lowered maximum orders of magnitude, therefore can further cut down the consumption of energy significantly by break is set.
If actuator also has middle power train (particularly planetary gear set or spur gear mechanism) and small gear, also is favourable.
The use of planetary gear set can make the compact to design of actuator.This is because might realize big velocity ratio in little installing space.This also is to realize for the inner member of middle power train (planetary gear set) is provided with extra supporting point on case of transmission owing to need not.Actuator also may be designed to elongated cylinder unit.Also feasible actuator is installed in favourable and simple mode of latter two reason becomes possibility on the case of transmission.
The use of spur gear mechanism can reduce axial installing space, because the gear stage that reduces gradually can be set abreast.But, the result be actuator tend to need be bigger radially installing space, that is to say that it is wideer that actuator becomes.But if more at radial zone internal ratio available installing space in axial region, that just may be favourable.
According to another kind of preferred implementation, break be arranged in parallel with respect to middle power train by the straight-tooth engagement.
Here also might reduce the axial installing space of actuator, this may be favourable according to the use condition in the power train.
If cam part is the central portion that tooth is arranged on the circular arc, also be useful.
In this way, cam part might drive by the corresponding teeth wheel shaft (band tooth axle) of motor or by the gear that is connected to motor.
According to further favourable improvement, cam part is connected to can be from the mechanically actuated Bowden cable of hull outside.
Make actuator no longer can get rid of this fault if during the adjustment cam parts, break down, then can utilize Bowden cable manually to recover cam part, particularly return to disengaged position by rotating cam parts forward or backward.This has in the mode of execution of integrated parking lock function especially favourable at cam part.Described feature is represented security feature and is used to guarantee release in case of emergency.
If under the installment state of actuating mechanism, actuator along the radial direction setting with respect to the disconnect-type clutch actuator shaft, also is favourable basically.
Described measure allows further to reduce required installing space.
Self evident is that above-mentioned feature and the feature that will illustrate hereinafter not only can be used in each combination that specifies, but also can be used in other combinations or use separately, do not deviate from protection scope of the present invention.
Description of drawings
Illustrative embodiments of the present invention has been shown in the accompanying drawing, and in the following description book, has introduced in further detail.In the accompanying drawings:
Fig. 1 shows the view of the part of exemplary dual-clutch transmission, wherein is equipped with according to actuating mechanism of the present invention;
Fig. 2 shows the shape of cam part according to the present invention in cylindrical coordinate system;
Fig. 3 shows the modification of the cam part among Fig. 2;
Fig. 4 shows the further modification of the cam part in Fig. 2 and 3;
Fig. 5 shows the functional diagram of the dual-clutch transmission under the parking lock function;
Fig. 6 shows the modification of the actuating mechanism among Fig. 1;
Fig. 7 shows the detailed view of the cam part among Fig. 6;
Fig. 8 shows the normal axomometric drawing figure according to the actuating mechanism of the joint support that is connected to dual-clutch transmission of the present invention;
Fig. 9 shows the vertical cross-section that passes Fig. 8, wherein also shows case of transmission;
Figure 10 shows another cross section of the actuating mechanism that passes among Fig. 8, considers additional case of transmission, wherein only shows the top of actuating mechanism;
Figure 11 a-c shows three kind of first modification of force compensating equipment;
Figure 12 a and b show two kinds of modification in addition of force compensating equipment;
Figure 13 shows the another kind of modification of the force compensating equipment of realizing on cam part; And
Figure 14 shows the stereogram of another kind of force compensating equipment.
Embodiment
In the following description to accompanying drawing, similar elements adopts identical reference character to represent.Distinct and revise place can describe.
Fig. 1 shows the partial view of dual-clutch transmission 10, and mechanism of the present invention wherein has been installed.Dual-clutch transmission 10 has housing 12.Yet the present invention is not limited to be installed in the dual-clutch transmission.The present invention can also be installed in single clutch speed changer or the clutch.The present invention also is suitable for use in wet clutch and the dry clutch.
Dual-clutch transmission 10 among Fig. 1 comprises the first clutch 14 with first leaf spring 16.Also be provided with second clutch 18 with second leaf spring 20.In first clutch 14 and the second clutch 18 each all constitutes the part of disconnect-type clutch 11.
First clutch 14 is used to activate first clutch and engages support 22.First clutch engage that support 22 is connected to first clutch 14 by leaf spring 16 and by leaf spring 16 along disengaged direction by preload.First clutch joint support 22 is installed so that it can be coaxial mobile with respect to first live axle 24 of inside, thus axially being moved along axle 24.
Second clutch 18 is connected to second clutch by second leaf spring 20 and engages support 26, and second clutch engages support 26 and movably is arranged on the second outside live axle 28.Second live axle 28 is with respect to first live axle, the 24 coaxial settings of inside.
Dual-clutch transmission 10 among Fig. 1 also has according to actuating mechanism 30 of the present invention.Actuating mechanism 30 comprises actuator 32, cam part 36 and particularly engage the clutch element of shift fork 42.
Under opposite movement direction, get final product holdback clutch.For this purpose, cam part 36 is along throwing off sense of rotation 54 (being counterclockwise in the case) rotation.The below part of shift fork 42 moves along disengaged direction 56 immediately, in the case for being moved to the left.The upper section of shift fork 42 moves along the direction of arrow 57 immediately, in the case for moving right.Described move cause successively by cam follower 46, and cam follower 46 is by moving with respect to cam part 36 radially outwards along the groove 40 of correspondingly-shaped.
Fig. 2 shows the cam part 36 self among Fig. 1.This figure adopts the form of cylindrical coordinate system, shows the whole circle around cam part 36 profiles thus, and this circle has marked from 0 to 330 ° angle.With regard to the groove among Fig. 1 40, groove 40 tilts by this way: engage sense of rotation 50 corresponding to counterclockwise throwing off sense of rotation 54 corresponding to clockwise direction.
The internal surface that is arranged in the groove 40 of Fig. 2 right-hand side constitutes so-called contact side 60.Because above-mentioned preload by 16,20 pairs of clutches of leaf spring, the cam follower 46 that is represented by dotted lines with contact side 60 and contact.Self evidently be, under the situation of oppositely preload, just because leaf spring 16,20 preload, direction of engagement 52 and disengaged direction 56 towards putting upside down, then contact surface 60 will be on the opposite sides of groove 40 (not illustrating in greater detail at this), and this side is arranged in the radially inner side of Fig. 2.
The physical dimension of groove 40 can preferably be chosen as and make the cam follower 46 with predetermined extent play can not be stuck in the groove.The shift fork roller can not have frictionally mobile effectively in groove 40.
Fig. 2 shows the engagement positio of cam part 36 and cam follower 46.Cam follower 46 radially moves inward from its normal position (referring to Fig. 1).If throw-out-of clutch, cam part 36 just along throwing off sense of rotation 54 clockwise direction rotation just, advance, so that cam follower 46 radially outwards move by the position from Fig. 2 so.
Fig. 3 shows a kind of modification according to the cam part 36 of Fig. 2, still at engagement positio.
This be shown as once more the position that is in Fig. 2 cam follower 46 since the preload of clutch 11 can move by radially outward, shown in arrow 74.Cam follower 46 is existing can not press to the contact side in the mode that tangent direction produces active force.In this way, just can reduce for clutch 11 is remained on jointing state the confining force that must apply by motor 33.At this, suppose that in the position of the cam follower 46 shown in Fig. 2 and Fig. 3 clutch 11 has been engaged reliably and described clutch 11 has been crossed the so-called bonding point that contacts side 60 thus reliably.
Therefore, by another recess 70, can reduce the power that clutch 11 is remained on jointing state that usually applies, therefore, engage support 22 and can move (referring to Fig. 1) slightly along disengaged direction 56 according to the mode of execution of the contact side 60 of Fig. 3 by actuator 32.This has just reduced energy consumption, and if actuator 32 be that fuel by vehicle provides energy, will reduce the consumption of fuel so especially.
Fig. 4 shows the further improvement of cam part 36, and with respect to the groove among Fig. 3, in the zone, bonding point, groove 40 is additionally strengthened once more, shown in bigger convex surface 76.Can be clear that with respect to reference circumference 72, the shape of contact side 60 is offset with respect to reference circumference 72 radially outwards once more.
Under the situation of dual-clutch transmission, shown in the embodiment among Fig. 1,, may and cam part 36 must be set in couples in order to activate clutch 14,18 simultaneously.If two grooves 40 all have relatively large convex surface 76, two clutches all may be engaged with described position in order to realize stopping lock function so.
Show the parking locked position by the embodiment among Fig. 5.Closed clutch and the transmission element of rhombus 80 expression, Fig. 5 shows two variable velocity zones of the dual-clutch transmission of gear 1-6 with reference numeral and reverse gear R.The clutch 14 and 18 that is provided with all is closed in each case in pairs.Here also have such situation: for example gear 1 and 2 that is to say that a gear of variable velocity zone will be engaged in each case.In the case, driving wheel can not move, because if one or two variable velocity zones all work with certain torque, so whole speed changer will be tauted.Can realize the lock function that stops in this way.If only engage a gear, then Dui Ying situation is applicable to single clutch.
As shown in Figure 4, the relatively large convex surface 76 of the groove 40 of cam part 36 has guaranteed that cam follower 46 (not shown in Fig. 4) can not directly be shifted out from its parking locked position.
For security reasons, in conjunction with the explanation of Fig. 4 and Fig. 5, may need to make the parking lock function also can be by release manually.For example, parked and under the situation that must be removed subsequently, because for example power failure or vehicle-mounted electric system fault make to activate when final controlling element can not or no longer can provide required power and may just need manual unlocking at vehicle.
For this reason, can utilize the Bowden cable (Bowden cable) 82 that provides among Fig. 6, this Bowden cable 82 be connected to cam part 36 and can be from case of transmission 12 externally actuated.Should notice that the cam part 36 that Fig. 6 illustrates among Fig. 1 once more has further convex surface 76, groove 40 extends down to the right from upper left once more, rather than as extending to left down from upper right in conjunction with the situation of Fig. 2-Fig. 4.Be further noted that groove 40 is the circumferencial direction extension along cam part basically.
Fig. 7 is used for illustrating especially the different piece of contact side 60.Contact side 60 is that locking or ' locked ' zone 76 and the insertion side 92 with corresponding protuberance constitute by working portion 86 in this case.Working portion 86 its upper end in Fig. 7 has bonding point 88 and has drop-outs 90 in its lower end.If cam part 36 is rotated to excessive degree along engaging sense of rotation 50, just need cross slight radially protuberance in the lateral parts 92 to enter ' locked ' zone 76.Pressure there is greater than the required power of complete closed clutch.Self evident is that in order to realize multiple function, the cam face among Fig. 2-Fig. 4 can be bonded to each other.
Fig. 8 shows the part stereogram of the dual-clutch transmission 10 shown in Fig. 1.Can be clear that actuating mechanism 30,30 according to paired setting of the present invention '.This be equally applicable to cam part 36,36 ', engage shift fork 42,42 ', first supporting member 38,38 ' and second supporting member 44,44 '.
Fig. 8 clearly show that the compact design of the actuating mechanism in the double clutch application 10.Actuator 32,32 ' be short structure radially with respect to live axle 24,28 (not shown here) with tangent direction.Driver 32,32 ' axle can relative to each other be provided with flexibly, in Fig. 8, relative to each other form and be approximately 160 ° angle.Angle between 150 ° to 160 ° is preferred.
Fig. 9 shows the perspective section view that runs through Fig. 8 central plane, wherein two actuating mechanisms 30,30 ' be connected to each other.In this can also be clear that the housing 12 that actuator 32 is integrated in well to be illustrated in addition.Very compact according to the structure of actuating mechanism 30 of the present invention, this has improved it and has been used for connecting the speed changer used or in the application of the speed changer of preceding horizontal layout.She Ji speed changer can be integrated in the serious limited usually speed changer passage of motor vehicle with simple and effective way by this way.
Figure 10 show the actuator 32,32 that runs through among Fig. 8 ' another sectional drawing, wherein, also shown case of transmission 12 in the drawings extraly for outstanding compact design.
At this, actuator 32 all has a motor 33, particularly electric motor in each case, the break 92 that is connected with motor 33 and be connected to the middle power train 94 (for example planetary gear set, spur gear mechanism etc.) of break 92.The driving pinion 96 of middle power train is preferably tooth Shape Design.Small gear 96 meshes with cam part 36 thus.
In the diagram of Figure 10, also can be clear that, be different from conventional design and only stretch out very little length from housing 12 according to the parts of actuating mechanism of the present invention.
Figure 11 a-Figure 11 c show three kinds of modification 100,100 of additional force canceller ' and 100 ", they all are connected to cam part 36 in each case.
Each force compensating equipment comprises that all an end is connected to the spring element 102 of cam part 36.In the modification of Figure 11 a and Figure 11 c, the other end of spring element 102 is fixed to housing 12.In the modification of Figure 11 b, housing 12 has opening, so that the other end of spring element 102 also can be fixed on the outside of housing 12.
In the modification of Figure 11 c, spring element 102 is engaged the rotation of sense of rotation 50 (being counter clockwise direction in the case) by preload to help cam part 36 edges at Figure 11 a.Guarantee that thus the power that is used for engaging clutch that must be applied by motor 33 is less than the power that must be applied by motor 33 when force compensating equipment 100 is not provided.
Figure 12 a and Figure 12 b show in addition two kinds of modification 100 " ' and 100 " of force compensating equipment ".Force compensating equipment 100 " ' and 100 " " be bonded on the joint shift fork 42, specifically be bonded on the bottom that engages shift fork 42.
Figure 13 shows the cam part 36 of the force compensating cam 106 with one, and force compensating cam 106 has constituted the radial outer side of another recess 108 in the prolongation main body of cam part 36 in the case.This cam part 36 has other alar part with respect to above-mentioned cam part 36, and this alar part comprises and is positioned at the recess 108 relative with the main body of aforesaid cam part 36.
At this, force compensating equipment represent with 110 and with Figure 11 b in force compensating equipment 100 ' be similar design, that is to say it is opening guiding by housing 12.Pressure spring 102 is preloaded between tension anchor pole 112 and the housing 12.Yet what should be mentioned in that at this is that tension anchor pole 112 needn't be guided through opening in the housing 12, but can also utilize with respect to the hard-wired roller of housing fixing with.
Figure 14 shows the further improvement of force compensating equipment 118, and it is similar to such and cam part 36 interactions among Figure 13.Cam part 36 among Figure 14 has the other recess 108 that has corresponding force compensating curve 116 equally.Force compensating equipment 118 comprises two pressure springs 102, and it under any circumstance all is tightened between the supporting point 120 and tension bearing 122 that is fixed with respect to housing.Tension bearing 122 is connected to the tension anchor pole 124 that is supported by supporting rollern 126, and supporting rollern 126 is arranged on the both sides of cam part 36 and extends on the screw rod 128 that is fixed with respect to housing.Force compensating equipment 118 produces the outer power 130 of radially pointing to haply.
Claims (23)
1, a kind of actuating mechanism that is used to engage and throw off the disconnect-type clutch of single clutch speed changer or multiple clutch speed-changer, described speed changer has the housing that is used for motor vehicle, and described actuating mechanism comprises:
Actuator;
Cam part, it has arc groove and can rotate around first supporting member, and described first supporting member is fixed with respect to described housing, and described cam part can be by described actuator along engaging sense of rotation or throwing off the sense of rotation rotation;
Engage shift fork, it can rotate around second supporting member, described second supporting member is fixed with respect to described housing, and a side of described shift fork is connected to described cam part by cam follower, the opposite side of described shift fork is connected to disconnect-type clutch, so that described disconnect-type clutch is closed and open when throwing off the sense of rotation rotation at described cam part when engaging the sense of rotation rotation at described cam part;
When the rotation of described cam part, described cam follower engages in the described arc groove and by the profile guiding of described arc groove;
When described actuator activated, described profile was formed as and makes the radial deflection of described cam follower along described cam part.
2, actuating mechanism as claimed in claim 1, the extending circumferentially of the described cam part in the basic upper edge of wherein said groove also has the radius of variation.
3, actuating mechanism as claimed in claim 1, wherein said groove has the contact side, and this contact side acts on the preload on the disconnect-type clutch owing to the disengaged direction along described disconnect-type clutch and contacts with described cam follower all the time under the installment state of described actuating mechanism.
4, actuating mechanism as claimed in claim 3, the cross section that wherein said contact side has one section spiral shape basically.
5, actuating mechanism as claimed in claim 4, wherein said helical are archimedes type.
6, actuating mechanism as claimed in claim 3, wherein said contacting side mask has continuous working portion, and this working portion has the bonding point and has drop-outs at its other end at the one end.
7, actuating mechanism as claimed in claim 6, wherein said contact side has convex surface in the zone at described bonding point.
8, actuating mechanism as claimed in claim 7, wherein said convex surface has constant radius.
9, actuating mechanism as claimed in claim 6, the lateral parts that wherein has protuberance is along disengaged direction in abutting connection with described working portion, and described lateral parts has the protuberance that is fused to basically in the lock section.
10, actuating mechanism as claimed in claim 9, wherein said lock section has constant radius.
11, actuating mechanism as claimed in claim 1 also comprises the force compensating equipment of the parts that are connected to described actuating mechanism, and the auxiliary described cam part of this force compensating equipment rotates along described joint sense of rotation.
12, actuating mechanism as claimed in claim 11, wherein said force compensating equipment is connected to one of described cam part and described shift fork.
13, actuating mechanism as claimed in claim 11, wherein said force compensating equipment has and the spring element of throwing off the reverse preload of sense of rotation, and an end of this spring element is connected to described housing and its opposite end is connected to one of described cam part and described shift fork.
14, actuating mechanism as claimed in claim 13, wherein when described spring element is connected to described cam part, described cam part has the protuberance of rising on it connects the outer surface of spring element, so that apply the power of maximum possible in the zone, bonding point at cam part along described joint sense of rotation rotation the time.
15, actuating mechanism as claimed in claim 1, wherein said cam follower rotatably is fixed on the shift fork roller between two prongs of described shift fork, and the diameter of this shift fork roller is selected to the shift fork roller can be moved along the play of the contact side in the described arc groove with predetermined extent.
16, actuating mechanism as claimed in claim 1, wherein said actuator has motor and break.
17, actuating mechanism as claimed in claim 16, wherein said motor is an electric motor.
18, actuating mechanism as claimed in claim 16, wherein said actuator also have middle power train and small gear.
19, actuating mechanism as claimed in claim 18, wherein said in the middle of power train be a kind of in planetary gear set and the spur gear mechanism, and described small gear have around ring gear.
20, actuating mechanism as claimed in claim 18, wherein said break be arranged in parallel with respect to power train in the middle of described by the straight-tooth engagement.
21, actuating mechanism as claimed in claim 1, wherein said cam part are the central portions that tooth is arranged on the circular arc.
22, actuating mechanism as claimed in claim 1, wherein said cam part are connected to can be from the mechanically actuated Bowden cable of described hull outside.
23, actuating mechanism as claimed in claim 1, wherein under the installment state of described actuating mechanism, described actuator is basically along the radially setting with respect to the actuator shaft of disconnect-type clutch.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102008013054A DE102008013054B4 (en) | 2008-03-06 | 2008-03-06 | Actuation mechanism for engaging and disengaging a separating clutch with a turnable segment |
| DE102008013054.0 | 2008-03-06 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101581341A true CN101581341A (en) | 2009-11-18 |
| CN101581341B CN101581341B (en) | 2012-08-08 |
Family
ID=40667167
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009102039310A Expired - Fee Related CN101581341B (en) | 2008-03-06 | 2009-03-06 | Adjustment mechanism for inserting and extracting a separation coupling with rotating curve segment |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US8191695B2 (en) |
| EP (1) | EP2098743B1 (en) |
| CN (1) | CN101581341B (en) |
| DE (1) | DE102008013054B4 (en) |
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| CN102619898A (en) * | 2012-03-30 | 2012-08-01 | 湖南大学 | Actuator for clutch |
| CN103047313A (en) * | 2011-09-06 | 2013-04-17 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Coupling assembly, motor vehicle power train and coupling actuation method |
| CN104110448A (en) * | 2013-04-19 | 2014-10-22 | 舍弗勒技术有限两合公司 | Clutch actuator |
| CN104141708A (en) * | 2013-05-07 | 2014-11-12 | 舍弗勒技术有限两合公司 | Clutch actuator |
| CN105992886A (en) * | 2014-02-12 | 2016-10-05 | 博格华纳扭矩输出系统公司 | An actuator for a dog clutch and a method for its control |
| CN107448502A (en) * | 2016-05-31 | 2017-12-08 | 法雷奥离合器公司 | Axial snap fit system for clutch mechanism |
| CN108884879A (en) * | 2016-04-08 | 2018-11-23 | 黑拉有限责任两合公司 | clutch actuation mechanism |
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| JP5461314B2 (en) * | 2010-06-08 | 2014-04-02 | 本田技研工業株式会社 | Clutch device |
| DE102010023840B4 (en) | 2010-06-09 | 2022-12-01 | Magna Pt B.V. & Co. Kg | Friction clutch arrangement for a motor vehicle drive train |
| US8758184B2 (en) | 2010-08-20 | 2014-06-24 | Redviking Group, Llc | Transmission test system |
| DE102011006969A1 (en) * | 2011-04-07 | 2012-10-11 | Zf Friedrichshafen Ag | Device for changing an operating state of at least one switching element |
| EP2532910B1 (en) | 2011-06-10 | 2013-08-21 | Hoerbiger Drivetrain Mechatronics B.V.B.A. | Friction clutch |
| US8905215B2 (en) | 2011-09-06 | 2014-12-09 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Clutch arrangement, motor vehicle drive train and clutch activation method |
| DE102011113278B4 (en) | 2011-09-06 | 2014-02-27 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Clutch assembly, automotive powertrain and clutch actuation method |
| FR2994239B1 (en) * | 2012-08-03 | 2014-08-08 | Valeo Embrayages | MECHANISM FOR CONTROLLING A CLUTCH FASTENING, IN PARTICULAR FOR A CLUTCH OF A MOTOR VEHICLE |
| DE102014207006A1 (en) | 2013-04-19 | 2014-10-23 | Schaeffler Technologies Gmbh & Co. Kg | clutch actuator |
| DE102013224958A1 (en) * | 2013-12-05 | 2015-06-11 | Robert Bosch Gmbh | Actuator for actuating a hydraulic clutch actuator and electrically actuated clutch |
| DE102015205952A1 (en) * | 2015-04-01 | 2016-10-06 | Robert Bosch Gmbh | Actuating device for actuating a hydraulic clutch actuator and clutch system |
| DE102016209425B3 (en) * | 2016-05-31 | 2017-11-09 | Schaeffler Technologies AG & Co. KG | Actuating device for a friction clutch and clutch system with this |
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| US1463445A (en) * | 1922-11-25 | 1923-07-31 | Standard Motor Construction Co | Power-transmission mechanism |
| EP1244879B1 (en) * | 1998-12-17 | 2012-09-05 | WABCO GmbH | Force applying device for wheel brakes |
| DE19947763C1 (en) * | 1999-10-02 | 2001-06-21 | Daimler Chrysler Ag | Actuator device for coupling or gear change box has servo transmission fixing part of change gear unit when uncoupled |
| GB0029058D0 (en) * | 2000-11-29 | 2001-01-10 | Meritor Light Vehicle Sys Ltd | Actuator |
| DE10235906A1 (en) * | 2002-08-06 | 2004-02-19 | Zf Sachs Ag | Torque transmission device in a motor vehicle |
| DE10252570B4 (en) | 2002-11-12 | 2014-09-25 | Zf Friedrichshafen Ag | Coupling system, in particular for motor vehicles, with at least one friction clutch and an actuating device |
| DE102004009832A1 (en) * | 2003-03-03 | 2004-09-16 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Disengaging system for a motor vehicle coupling or brake has lever with support point which is displaceable to adjust the operating force on the coupling |
| US7150348B2 (en) * | 2003-10-07 | 2006-12-19 | Magneti Marelli Powertrain Usa Llc | Ergonomic clutch actuator |
| DE102006015885A1 (en) * | 2005-04-28 | 2006-11-02 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Rocker lever actuator for operating clutch of vehicle, has operating lever exerting variable actuating force for opening and closing of clutch and comprising contour at surface that stands in contact with pivotal point of operating lever |
| EP1744076B1 (en) * | 2005-04-28 | 2009-12-16 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Rocking lever actuator, in particular for actuating a clutch |
| EP1937990A1 (en) * | 2005-09-26 | 2008-07-02 | Ricardo Uk Limited | Control assembly |
| FR2896288B1 (en) * | 2006-01-17 | 2010-03-12 | Valeo Embrayages | ACTUATOR WITH EFFORT COMPENSATION, IN PARTICULAR FOR A CLUTCH OF A MOTOR VEHICLE |
| DE102006008226A1 (en) * | 2006-02-22 | 2007-08-23 | Robert Bosch Gmbh | Double clutch for a double clutch transmission of a motor vehicle comprises an electrical regulator acting on a curved body which operates both clutches and controls a coupling process between the clutches of a double clutch transmission |
-
2008
- 2008-03-06 DE DE102008013054A patent/DE102008013054B4/en not_active Expired - Fee Related
-
2009
- 2009-02-27 EP EP09153850A patent/EP2098743B1/en not_active Expired - Fee Related
- 2009-03-06 CN CN2009102039310A patent/CN101581341B/en not_active Expired - Fee Related
- 2009-03-06 US US12/399,890 patent/US8191695B2/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103047313A (en) * | 2011-09-06 | 2013-04-17 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Coupling assembly, motor vehicle power train and coupling actuation method |
| CN103047313B (en) * | 2011-09-06 | 2016-09-14 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Clutch apparatus and actuating method thereof |
| CN102619898A (en) * | 2012-03-30 | 2012-08-01 | 湖南大学 | Actuator for clutch |
| CN104110448A (en) * | 2013-04-19 | 2014-10-22 | 舍弗勒技术有限两合公司 | Clutch actuator |
| CN104110448B (en) * | 2013-04-19 | 2018-03-09 | 舍弗勒技术股份两合公司 | Clutch actuator |
| CN104141708A (en) * | 2013-05-07 | 2014-11-12 | 舍弗勒技术有限两合公司 | Clutch actuator |
| CN104141708B (en) * | 2013-05-07 | 2018-10-12 | 舍弗勒技术股份两合公司 | Clutch actuating mechanism |
| CN105992886A (en) * | 2014-02-12 | 2016-10-05 | 博格华纳扭矩输出系统公司 | An actuator for a dog clutch and a method for its control |
| CN108884879A (en) * | 2016-04-08 | 2018-11-23 | 黑拉有限责任两合公司 | clutch actuation mechanism |
| CN108884879B (en) * | 2016-04-08 | 2020-09-08 | 黑拉有限责任两合公司 | Clutch actuating mechanism |
| CN107448502A (en) * | 2016-05-31 | 2017-12-08 | 法雷奥离合器公司 | Axial snap fit system for clutch mechanism |
| CN107448502B (en) * | 2016-05-31 | 2020-08-04 | 法雷奥离合器公司 | Axial engagement system for a clutch mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102008013054A1 (en) | 2009-09-10 |
| US8191695B2 (en) | 2012-06-05 |
| EP2098743A1 (en) | 2009-09-09 |
| DE102008013054B4 (en) | 2010-04-22 |
| CN101581341B (en) | 2012-08-08 |
| EP2098743B1 (en) | 2012-04-18 |
| US20100187067A1 (en) | 2010-07-29 |
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